EP3011196A2

EP3011196A2 - Transmission device for a motor vehicle

Info

Publication number: EP3011196A2
Application number: EP14744764.3A
Authority: EP
Inventors: Markus Brandenburg; Tobias Härter; Markus Rossmeier; Nils Tonius
Original assignee: Daimler AG
Current assignee: Mercedes Benz Group AG
Priority date: 2013-06-22
Filing date: 2014-06-13
Publication date: 2016-04-27
Anticipated expiration: 2034-06-13
Also published as: EP3011196B1; US20160160936A1; EP3011199B1; DE102013011555A1; JP6144830B2; CN105324587A; WO2014202195A2; EP3011200A1; DE102013011569A1; US20160138706A1; CN105324591A; WO2014202210A1; US9964159B2; DE102013011567A1; US9939028B2; DE102013011566A1; WO2014202211A1; CN105229337A; WO2014202211A8; CN105324587B

Abstract

The invention relates to a transmission device for a motor vehicle, comprising at least one coupling unit (S2a; S2b; S2c), which has a friction-closure unit (13a; 13b; 13c) and a form-closure unit (14a; 14b; 14c) connected in parallel with the friction-closure unit (13a; 13b; 13c) in order to connect two coupling elements (S21a, S22a) in a rotationally fixed manner, a first hydraulic and/or pneumatic actuator (15a; 15b; 15c) for actuating the form-closure unit (14a; 14b; 14c), a second hydraulic and/or pneumatic actuator (16a; 16b; 16c) for actuating the friction-closure unit (13a; 13b; 13c), and a directional control valve (17a; 17b; 17c) for controlling the first actuator (15a; 15b; 15c) provided for actuating the form-closure unit (14a; 14b; 14c), wherein the directional control valve (17a; 17b; 17c) has a control line connection (18a; 18b; 18c), which in at least one operating state is connected, with respect to pressure, to the second actuator (16a; 16b; 16c) provided for actuating the friction-closure unit (13a; 13b; 13c).

Description

Transmission device for a motor vehicle

The invention relates to a transmission device according to the preamble of claim 1.

From DE 10 2011 108 024 A1 is already a transmission device for a

Motor vehicle, with a coupling unit for non-rotatable connection of two

Coupling a Reibschlusseinheit and a parallel to the Reibschlusseinheit switched form-locking unit, with a first hydraulic actuator for actuating the form-locking unit, with a second hydraulic actuator for actuating the Reibschlusseinheit and with a directional control valve for controlling the first actuator, known.

The invention is in particular the object of improving the control of the first actuator. This object is achieved by an inventive

Gear device solved according to claim 1. Further developments of the invention will become apparent from the dependent claims.

The invention is based on a transmission device for a motor vehicle, with at least one coupling unit which, for the rotationally fixed connection of two coupling elements, has a friction-locking unit and a parallel connection to the friction-locking unit

Form-fitting unit having a first hydraulic and / or pneumatic actuator for actuating the form-locking unit, with a second hydraulic and / or pneumatic actuator for actuating the Reibschlusseinheit and with a directional control valve for controlling the intended for actuating the form-locking unit first actuator. In the context of the invention is under a parallel to a Reibschlusseinheit

switched form-locking unit understood in the power flow to a Reibschlusseinheit connected in parallel Formschlusseinheit. With a coupling unit which has a friction-locking unit and a form-locking unit connected in parallel with the friction-locking unit for the rotationally fixed connection of two coupling elements, these are

CONFIRMATION COPY Coupling elements both by closing the Reibschlusseinheit and by closing the form-locking unit and by closing the

Reibschlusseinheit and the form-fitting unit rotatably connected.

It is proposed that the directional control valve has a control line connection which, in at least one operating state, is connected by pressure to the one for actuating the

Frictional engagement unit provided second actuator is connected. By the pressure-technical connection of the control line connection of the directional control valve to the provided for actuation of the Reibschlusseinheit second actuator, the control of the

Actuation of the form-locking unit provided first actuator in response to the operation of the Reibschlusseinheit done, which can be realized that the form-fitting unit is closed only when the Reibschlusseinheit is closed. As a result, it can be prevented that the positive locking unit is closed in an unsynchronized state, as a result of which the positive locking unit is convenient and

can be closed with little wear. The first actuator provided for actuating the form-locking unit can be actuated as a function of a louver actuation pressure provided for actuating the frictional engagement unit connected in parallel, whereby a reliable criterion for closing the form-fitting unit can be provided in a particularly simple manner. As a result, a comfortable and low-wear closing of the form-locking unit can take place reliably, as a result of which the activation of the first actuator provided for actuating the form-locking unit can be improved. A "coupling unit" is to be understood in particular as meaning both a clutch and a brake. "Coupling" is to be understood in particular as meaning a unit which is provided to selectively connect two rotatably arranged coupling elements to one another or to separate them from one another. A "brake" is to be understood in particular a unit which is intended to rotatably connect a rotatable coupling element and a fixed coupling element, which is preferably permanently connected rotationally fixedly connected to a fixed component or integrally formed therewith, or to separate from each other The stationary component is advantageously designed as a transmission housing of the transmission device. A "friction locking unit" should be understood to mean, in particular, a unit which essentially produces the rotationally fixed connection by a frictional connection, such as a multi-plate clutch or a multi-disc brake. A "form-locking unit" is to be understood in particular as a unit which holds the rotationally fixed connection in the

Essentially produced by a positive connection, such as a

Claw clutch or a claw brake. The Reibschlusseinheit and the Form-fitting units are preferably operative between the two

Coupling elements arranged. Under a "control line connection" should

In particular, a hydraulic or pneumatic fluid connection can be understood, which is provided for switching the directional control valve and / or for

Betriebsmitteldruckbeaufschlagung a control volume of the directional control valve

is technically connected to the control volume. In the context of the invention, a control volume is preferably to be understood as a volume limited by a valve housing of the directional control valve and a control surface of a valve spool of the directional control valve which is movable in the valve housing. A ruling in the control volume

Operating medium pressure preferably acts on the control volume limiting

Control surface of the valve spool, whereby the valve spool, with a corresponding Betriebsmitteldruckbeaufschlagung in the valve housing moves. A "pressure-technical connection" is to be understood in particular as meaning a hydraulic or pneumatic connection between at least two connection partners, by means of which at least substantially the same operating medium pressure is present at, in and / or between the connection partners, at least in a hydrostatic operating state specially trained, programmed, equipped, designed and / or arranged to be understood. The inventive

Control line connection, which is connected in at least one operating state by printing technology with the second actuator provided for actuating the friction-locking unit, is provided for the purpose of controlling the control volume, which is associated with the printing technology

Control line connection is connected, with the lamella actuation pressure

can be acted upon. The vane actuation pressure acts on the control volume limiting control surface for the vane actuation pressure of the valve spool of the directional control valve.

In one embodiment of the invention it is proposed that the directional control valve has a second control line connection, which is connected in terms of printing technology in at least one operating state with the first actuator provided for actuating the form-fitting unit. As a result, one for actuating the form-locking unit

provided Klauenbetätigungsdruck and provided for actuating the parallel-connected Reibschlusseinheit lamellar actuation pressure for driving the

Directional valve can be used, whereby the control of the first actuator can be optimized. The control line connections of the directional control valve are preferably assigned in each case to a control volume, and are provided for operating medium pressure of a respective control volume, wherein the control volumes are separated from each other by printing technology. The second control line connection according to the invention, which is connected in at least one operating state by printing technology with the provided for actuating the form-locking unit first actuator, is provided for that the control volume, which is connected by pressure to the second control line, can be acted upon with the jaw operating pressure. Of the

Claw actuation pressure acts on the control volume, which is connected by pressure to the second control line connection limiting control surface of the valve spool of the directional control valve.

In a further embodiment of the invention, it is advantageous if the directional control valve has a valve slide with two, each one of the control line connections associated control surfaces, wherein the control surfaces are oriented in the same direction. As a result, when the form-locking unit is closed, a valve position of the directional control valve which is set by the lamella actuating pressure provided for actuating the friction-locking unit can be provided by the valve unit for actuating the form-locking unit

Claw actuation pressure can be maintained, and the vane actuation pressure can, for example, for dissolving a tooth-on-tooth position in the

Formschlusseinheit be lowered without the directional control valve by the

Slat actuation pressure set valve position leaves. In principle, it can also be realized in an advantageous manner that the claw actuation pressure is used to hold the valve position set by the slat actuation pressure, whereby the frictional engagement unit can be opened after closing the form fit unit. By a "control line connection associated control surface" should be understood in particular a control surface which limits a control volume, which Druckmittisch the Betriebsmitteldruckbeaufschlagung with the

Control line connection is connected, whereby preferably one on the

Control line connection applied operating fluid pressure in the control volume prevails and thus acts on the control surface. By "control surfaces oriented in the same direction" is meant in particular that surface normals of one control surface and surface normals of the other control surface are directed in the same direction

Betriebsmitteleldruckeinwirkung preferably for valve spool movement for a

Setting the same valve position of the directional valve provided. A

Equipment pressurization of control volumes associated with control surfaces oriented in the same direction causes movement of the valve spool in the same direction. A "surface normal" should in particular be understood to mean a direction vector which is arranged orthogonally on a surface and directed away from it. In a further embodiment of the invention, the directional control valve has at least one third control line connection and the valve slide one the third

Control line connection associated control surface, which to the other

Control surfaces of the valve spool is oriented in the opposite direction. By additionally provided in this embodiment of the invention third

Control line connection with the third control line connection associated control surface of the valve spool of the directional control valve is advantageously acted upon by an additional third control pressure and the valve position is adjustable in dependence on the third control pressure. In particular, in a transmission device with a further coupling unit, which is also controlled by the directional control valve can be avoided by the possible admission of the valve spool of the directional control valve with a third control pressure conflicts for the control of the further coupling unit through the directional valve, which realizes particularly comfortable transmission gear shifts can be. The others

Coupling unit, which is also driven by the directional control valve, is referred to in the context of the invention as the second additional coupling unit. It can by the possible admission of the valve spool of the directional control valve with a third

Control pressure conflicts for the control of the second additional coupling unit in a transmission gear shift from an actual gear in which the coupling unit

is closed, in a target gear, in which the second further coupling unit is closed, can be avoided. Furthermore, with a

Betriebsmitteldruckbeaufschlagung the third control surface on the third

Control line connection a spring of the directional control valve are supported, whereby the spring can be advantageously designed for small spring forces. Under a control surface, which is "oriented to the other control surfaces in the opposite direction" should be understood in particular that surface normals of the control surface and

Surface normals of the other control surfaces are directed in opposite directions to each other. The oppositely-oriented control surfaces are preferably provided for operating valve pressure for valve spool movement for adjustment of opposite valve positions of the directional control valve.

In a further embodiment of the invention, the transmission device has a

Solenoid valve and a third actuator for actuating a first further

Coupling unit, wherein the first further coupling unit is connected in at least one operating condition by printing technology with the third control line connection, whereby one provided for actuating the third coupling unit Operating fluid pressure can be used as the third control pressure for setting the directional control valve. Under the fact that a "solenoid valve has an ... Actuator for actuating a ... coupling unit" is understood in the context of the invention that a

Solenoid valve controls an actuator and the actuator then according to the

Control specifications by the solenoid valve actuates the coupling unit. The

Provision of the third control line connection, which is connected to the third actuator for actuating the first further coupling unit by means of printing, advantageously enables adjustability of a Betriebsmittelelddruckbeaufschlagung the third control line connection via the solenoid valve, which for a

Operating medium pressure adjustment is provided in the third actuator for actuating a first further coupling unit of the transmission device. Advantageously, the operating medium pressure set by the solenoid valve is thus not only for the actuation of the first further coupling unit, but also for a control of the

Forming unit usable. According to the invention acts on the valve spool of the

Directional valve provided for operating the Reibschlusseinheite

Slat actuation pressure as a control pressure that is used to actuate the

Forming closure unit provided claw operation pressure as the second control pressure and provided for actuating the first further coupling unit

Operating medium pressure as the third control pressure. Advantageously, the directional control valve according to the invention is designed so that the valve spool of the directional control valve provided for actuating the first further coupling unit operating medium pressure to

Operation of the form-locking unit provided claw operation pressure and provided for actuating the parallel-connected Reibschlusseinheit

Counteracts lamellar actuation pressure.

In a further embodiment of the invention, the directional control valve has at least one spring whose spring force is oriented in the same direction as the

Control surface, which is assigned to the third control line connection of the valve spool. Is the solenoid valve and the third actuator for actuating the first further coupling unit provided in the transmission device according to the invention, wherein the first further coupling unit is connected in at least one operating condition by pressure with the third control line connection, and act for the operation of the first further coupling unit provided operating medium pressure and the spring force to the

Slat actuation pressure against, so can advantageously a degree of cross-influences on the further control system of the transmission device, by a control the directional control valve, be kept small, which is explained in more detail for an embodiment of the invention.

In a further embodiment of the invention, the first further coupling unit is closed in a fourth, fifth, sixth, seventh, eighth and ninth forward gear and the coupling unit in the eighth forward gear, in the ninth forward gear and in a reverse gear closed. Is in the transmission device according to this embodiment of the invention, the solenoid valve and the third actuator for actuating the first further coupling unit provided, wherein the first further coupling unit is connected in at least one operating condition by pressure with the third Steuerleltungsanschluss, and act for the operation of the first further coupling unit provided Operating medium pressure and the spring force provided for the operation of the form-locking unit claw actuation pressure and provided for actuating the parallel-connected Reibschlusseinheit

Slat actuation pressure against, it is advantageous to control the

Positive locking unit with the directional control valve according to the invention in reverse control technology simple. In the transmission device according to this embodiment of the invention, the control volume of the directional control valve, which is bounded by the control surface, which is assigned to the third Steuerleltungsanschluss is depressurized in reverse.

In a further embodiment of the invention, the transmission device has a

Working pressure system, which is connected in at least one operating condition by pressure with the third control connection terminal. This allows the directional valve in

Dependence of the working pressure can be switched, whereby the intended for the actuation of the positive locking unit first actuator in dependence of the working pressure, the vane actuation pressure and the claw actuation pressure can be controlled. On the valve spool acts according to the invention as a control pressure to

Actuation of the Reibschlusseinheit provided slat actuation pressure, as the second control pressure provided for actuating the form-locking unit

Claw actuation pressure and as third control pressure the working pressure. In this case, the working pressure advantageously acts on the claw actuating pressure provided for actuating the form-locking unit and on the operation of the parallel-connected claw actuating pressure

Reibschlusseinheit provided slat actuation pressure against. In the context of the invention is meant by the working pressure system, the equipment pressure system for the transmission device, which is provided for driving the coupling units of the transmission device. The height of the working pressure of the Work pressure system with the required pressure, which is for a

Keeping closed the coupling units at maximum torque requirements is required.

Furthermore, it is proposed that the directional control valve has at least one spring whose spring force is oriented in the opposite direction, as the control surface of the valve spool, which is assigned to the third control line connection. In particular, the spring can thereby provide the lamellar actuation pressure provided for actuation of the friction-locking unit and / or the claw actuation pressure provided for actuation of the positive-locking unit for the valve-slide movement against the

Support working pressure, which can be realized that the spring the

Directional valve switches to a selected valve position when the

Slat actuation pressure and / or the claw actuation pressure is the same as the working pressure. The control surface and the spring whose spring force in terms of

Switching direction to the control surface, which is associated with the third control line connection, is opposite, are preferably for valve spool movement in

provided opposite directions. The spring, whose spring force with respect to the switching direction to the control surface, which is assigned to the third control line terminal, is opposite, and acting on the control surface operating medium pressure act for valve spool movement preferably in opposite valve positions. Thus, according to the invention, the working pressure acts to actuate the

Form-fitting unit provided claw actuation pressure, which opposes the operation of the parallel-connected Reibschlusseinheit slat actuation pressure and the spring force.

It is further proposed that the transmission device has a further solenoid valve and a fourth actuator for actuating a second further coupling unit, wherein the directional control valve has a first working line connection to which the first actuator is connected, and a second working line connection to which the fourth actuator is connected. having. This allows the further solenoid valve for both

Actuation of the form-locking unit can be used as well as for actuation of the second further coupling unit, whereby a number of solenoid valves and thus a complexity in the transmission device can be kept low. A "working line connection" should in particular be understood to mean a hydraulic or pneumatic connection which is used to supply the operating medium to at least one component of the transmission device or of the motor vehicle, in particular of a coupling unit the transmission device is provided, preferably to actuate these to cool and / or lubricate.

In this embodiment of the invention, a set valve position of the

Directional valve, in which the further solenoid valve is connected to the first actuator for actuating the form-locking unit, only with the for actuating the

Forming claw unit provided claw operation pressure can be maintained so that the slat actuation pressure, for example, to dissolve a tooth-on-tooth position of the positive locking unit, can be lowered without the directional control valve leaves the set valve position. This can be a tooth-on-tooth position of

Positive locking unit advantageously be solved in this embodiment of the invention.

In a further embodiment of the invention, the transmission device has a

Switching valve, which is provided to connect the pressure for the connection to the second actuator control line connection with the first actuator. Advantageously, by providing the switching valve, the provision of a control surface on the valve spool, which is assigned only to the second control line connection, be avoided, whereby a structurally simple and production-cost-effective directional control valve can be provided without a stepped valve spool.

In principle, in the presence of only one control line connection provided for the first actuator and the second actuator, it can also be realized that the claw actuation pressure is used to hold the valve position set by the slat actuation pressure, whereby the frictional connection unit can be opened after closing the form fit unit.

Further advantages will become apparent from the following description of the figures. In the figures, three embodiments of the invention are shown. The figures, the

Description of the figures and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

Showing:

Fig. 1 shows schematically a transmission device for a motor vehicle, a

Combined coupling unit having a Reibschlusseinheit and a form-locking unit,

2 is a circuit diagram of the transmission device, 3 shows the combined coupling unit with a first actuator for actuating the form-locking unit and a second actuator for actuating the

Reibschlusseinheit,

4 shows schematically an actuation of the actuators,

5 shows an alternative trained actuation of the actuators and

6 shows a third embodiment of an actuation of the actuators.

FIG. 1 partially shows a transmission device of a motor vehicle which forms part of a motor vehicle drive train. The transmission device is provided for an automatic transmission. The motor vehicle having the transmission device has an internal combustion engine, not shown, for driving the motor vehicle and drive wheels not shown in detail. To set ten gears V1-V9, R, the transmission device has a gear set 63a. The gear set 63a is arranged in a power flow between the engine and the drive wheels.

The gear set 63a has nine forward gears V1-V9 and one reverse gear R. The forward gears V1-V9 have successive gear ratios. Here, the first forward gear V1 has the largest gear ratio and the last, in this embodiment ninth forward gear V9, the smallest gear ratio, the gear ratios decrease from low to high forward gear V1 -V9. The reverse gear R has a direction of rotation reversal compared to the forward gears V1 -V9. The gear set 63a can be connected to a hybrid drive module by means of which a drive torque can be changed. Further, by means of the hybrid drive module and the gear set 63a, a CVT can be realized, whereby the gear ratio can be adjusted continuously, at least in some areas. The transmission device is configured as a multi-stage transmission device.

The transmission device further comprises a transmission housing 31 a, which is arranged stationary. The gear set 63a is disposed within the gear housing 31 a.

To initiate a drive torque provided by the internal combustion engine in the gear set 63a, the transmission device has a transmission input shaft 64a. The transmission input shaft 64a is in a starting from the internal combustion engine arranged the power flow after the drive motor and in front of the gear set 63a. The transmission input shaft 64a may be preceded by a module not shown in detail, which in particular provides a start-up functionality. As an upstream module, for example, a torque converter or a wet starting clutch is conceivable. In principle, however, the module provided for starting can also be integrated in the gear set 63a.

To derive a translated drive torque, the transmission device has a transmission output shaft 65a. The transmission output shaft 65a is disposed in the power flow from the engine after the gear train 63a and before the drive wheels. The transmission output shaft 65a may be followed by a module not shown in detail, by means of which the output from the gear set 63a drive torque can be distributed to the drive wheels, such as a planetary gear, which is provided for a speed compensation between the drive wheels, or an all-wheel drive unit, the drive torque distributed on two different drive axles. The transmission input shaft 64a and the transmission output shaft 65a can basically be arranged arbitrarily to one another.

The gear set 63a has four planetary gear Pia, P2a, P3a, P4a, which are operatively connected to each other to the circuit of the gears V1-V9, R. The first planetary gear stage Pi a, the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a are arranged one behind the other along a main axis of rotation 66a. An axis of rotation of the transmission input shaft 64a coincides with the main rotation axis 66a. All planetary gear stages Pi a, P2a, P3a, P4a of the gear set 63a have a Einfachplanetenradsatz. The terms "first", "second", "third" and "fourth" indicate an axial order of the planetary gear stages Pia, P2a, P3a, P4a from the internal combustion engine. Accordingly, the first planetary gear stage Pi a compared to the other planetary gear P2a, P3a, P4a at the first axial position, the second planetary gear P2a compared to the other planetary gear stages Pia, P3a, P4a at the second axial position, the third planetary gear P3a compared to the other planetary gear stages Pi a, P2a, P4a arranged at the third axial position and the fourth planetary gear P4a compared to the other planetary gear stages Pi a, P2a, P3a at fourth axial position.

The four planetary gear stages Pia, P2a, P3a, P4a are described in more detail below. The four planetary gear stages Pi a, P2a, P3a, P4a each have a sun gear, a planetary carrier and a ring gear. It should simplify under a "first to fourth planetary gear carrier ", a" first to fourth sun gear "and a" first to fourth ring gear "one of the first to fourth planetary gear stage Pi a, P2a, P3a, P4a associated planet carrier or a sun gear or a ring gear are understood, ie, for example, that under the first planet carrier a planet carrier of ers th planetary gear Pi a is to be understood.

The first planetary gear stage Pi a is arranged on the input side. The first planetary gear stage Pi a comprises a first sun gear P1 1 a, a first ring gear P13a and a first planet carrier P12a. The first planet carrier P12a leads planetary gears P14a of the first planetary gear Pi a on a circular path. The planetary gears P14a mesh with the first sun gear P1 1 a and with the first ring gear P13a. The planetary gears P14a are rotatably supported on the first planet carrier P12a.

The second planetary gear P2a is arranged centrally on the input side. The second planetary gear P2a includes a second sun gear P21a, a second ring gear P23a, and a second planetary gear carrier P22a. The second planet carrier P22a leads planetary gears P24a of the second planetary gear P2a on a circular path. The planet gears P24a mesh with the second sun gear P21a and with the second ring gear P23a. The planetary gears P24a are rotatably supported on the second planet carrier P22a.

The third planetary gear P3a is arranged centrally on the output side. The third planetary gear P3a includes a third sun gear P31a, a third ring gear P33a, and a third planetary gear P32a. The third planet carrier P32a leads planetary gears P34a of the third planetary gear P3a on a circular path. The planetary gears P34a mesh with the third sun gear P31a and with the third ring gear P33a. The planetary gears P34a are rotatably supported on the third planet carrier P32a.

The fourth planetary gear P4a is arranged on the output side. The fourth

Planetary gear stage P4a includes a fourth sun gear P41a, a fourth ring gear P43a, and a fourth planetary gear carrier P42a. The fourth planet carrier P42a leads

Planet wheels P44a the fourth planetary gear P4a on a circular path. The

Planet gears P44a mesh with the fourth sun gear P41a and with the fourth ring gear P43a. The planet gears P44a are rotatably supported on the fourth planet carrier P42a.

The first ring gear P13a is permanently connected in a rotationally fixed manner to the second planet carrier P22a. The second ring gear P23a is permanently non-rotatable with the third sun gear P31 a and permanently rotatably connected to the fourth sun P41 a. The third sun P31 a and the fourth sun P41 a are permanently connected to each other rotatably. To initiate the drive torque provided by the internal combustion engine, the first planetary gear stage Pia and the fourth planetary gear stage P4a are each designed as an input stage. To form the first planetary gear stage Pi a as input stage, the first sun gear P1 1a is permanently connected in a rotationally fixed manner to the transmission input shaft 64a. To form the fourth planetary gear P4a as an input stage of the fourth planetary gear P42a permanently rotatably connected to the transmission input shaft 64a. For discharging the drive torque translated by the gear set 63a, the third planetary gear P3a and the fourth planetary gear P4a are each formed as an output stage. To form the third planetary gear P3a as the output stage of the third planetary gear P32a permanently non-rotatably connected to the transmission output shaft 65a. To form the fourth planetary gear P4a as an output stage, the fourth ring gear P43a is rotatably connected to the transmission output shaft 65a.

To shift the gears V1-V9, R, the transmission device has six coupling units S1a, S2a, S3a, S4a, S5a, S6a. The coupling units S1 a, S2a, S3a, S4a, S5a, S6a are each formed as a switching unit, which are provided for switching the gears V1-V9, R. The coupling units S1 a, S2a, S3a, S4a, S5a, S6a are provided to either rotatably connect two optional rotatable transmission elements together and separate from each other or optionally rotatably connect a rotatable transmission element with the transmission housing 31 a or to be separated from this. A gear element is a sun gear P1 1a, P21 a, P31 a, P41 a, a planet P12a, P22a, P32a, P42a or a ring gear P13a, P23a, P33a, P43a.

The three coupling units S a, S3 a, S 6 a are each formed as a coupling. They each have a first rotatable coupling element S1 1 a, S31 a, S61 a and a second rotatable coupling element S12a, S32a, S62a. The three coupling units S1 a, S3a, S6a are each intended to rotatably connect their two rotatable coupling elements S1 1 a, S12a, S31a, S32a, S61a, S62a.

The three coupling units S2a, S4a, S5a are each designed as a brake. They each have a rotatable coupling element S21a, S41a, S51a and a fixed, housing-fixed coupling element S22a, S42a, S52a. The coupling units S2a, S4a, S5a are each provided to their rotatable coupling element S21 a, S41 a, S51 a and their fixed coupling element S22a, S42a, S52a rotatably connected to each other. They are each intended to their rotatable coupling element S21 a, S41 a, S51 a fixed to the housing and thus rotatably connected to the transmission housing 31 a.

The first coupling unit S1 a has the first rotatable coupling element S1 1 a and the second rotatable coupling element S12a. The first rotatable coupling element S1 1 a of the first coupling unit S1 a is permanently non-rotatably connected to the transmission input shaft 64a. The second rotatable coupling element S12a of the first coupling unit S1a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a of the second coupling unit S2a. The second rotatable coupling element S12a of the first coupling unit S1a is further permanently non-rotatably connected to the first planetary gear P12a. The first coupling unit S1 a is provided for non-rotatably connecting the first planet carrier P12a to the transmission input shaft 64a. The coupling unit S1 a has for the rotationally fixed connection of the rotatable coupling elements S1 1 a, S12a only one Reibschlusseinheit 38a. The coupling unit S1a is designed as a multi-plate clutch. The friction-locking unit 38a comprises a disk pack for the rotationally fixed connection of the coupling elements S11a, S12a.

The second coupling unit S2a has the rotatable coupling element S21a and the fixed coupling element S22a. The rotatable coupling element S21 a of the second coupling unit S2a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. Furthermore, the rotatable coupling element S21a of the second coupling unit S2a is permanently connected in a rotationally fixed manner to the first rotatable coupling element S31a of the third coupling unit S3a. The fixed coupling element S22a of the second coupling unit S2a is permanently connected in a rotationally fixed manner to the transmission housing 31a. The fixed coupling element S22a of the second coupling unit S2a is formed integrally with the transmission housing 31a. The coupling unit S2a is provided to rotatably connect their rotatable coupling element S21a and their fixed coupling element S22a with each other. The second coupling unit S2a is provided to connect the first planet carrier P12a fixed to the housing.

The third coupling unit S3a has the first rotatable coupling element S31a and the second rotatable coupling element S32a. The first rotatable coupling element S31 a of the third coupling unit S3a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. The second rotatable coupling element S32a of the third coupling unit S3a is permanently non-rotatably connected to the second ring gear P23a. The second rotatable coupling element S32a of the third coupling unit S3a is further permanently non-rotatably connected to the third sun P31 a and permanently rotatably connected to the fourth sun P41 a. The third coupling unit S3a is provided for non-rotatably connecting the first planet carrier P12a, the second ring gear P23a, the third sun gear P31a and the fourth sun gear P41a. The coupling unit S3a is designed as a multi-plate clutch. It merely has a frictional engagement unit, which comprises a disk pack for the rotationally fixed connection of the coupling elements S31a, S32a.

The fourth coupling unit S4a has the rotatable coupling element S41a and the fixed coupling element S42a. The rotatable coupling element S41 a of the fourth coupling unit S4a is permanently non-rotatably connected to the second sun gear P21 a. The fixed coupling element S42a of the fourth coupling unit S4a is permanently non-rotatably connected to the transmission housing 31a. The fourth coupling unit S4a is provided to connect the second sun gear P21a fixed to the housing. The coupling unit S4a is designed as a multi-disc brake. It merely has a frictional engagement unit, which comprises a disk pack for the rotationally fixed connection of the coupling elements S41a, S42a.

The fifth coupling unit S5a has the rotatable coupling element S51a and the fixed coupling element S52a. The rotatable coupling element S51a of the fifth coupling unit S5a is permanently non-rotatably connected to the third ring gear P33a. The fixed coupling element S52a of the fifth coupling unit S5a is permanently non-rotatably connected to the transmission housing 31a. The fifth coupling unit S5a is provided to connect the third ring gear P33a fixed to the housing. The coupling unit S5a is designed as a multi-disc brake. It merely has a friction-locking unit, which comprises a disk pack for the rotationally fixed connection of the coupling elements S51a, S52a.

The sixth coupling unit S6a has the first rotatable coupling element S61a and the second rotatable coupling element S62a. The first rotatable coupling element S61 a of the sixth coupling unit S6a is permanently non-rotatably connected to the fourth ring gear P43a. The second rotatable coupling element S62a of the sixth coupling unit S6a is permanently connected in a rotationally fixed manner to the third planet carrier P32a. The second rotatable coupling element S62a of the sixth coupling unit S6a is further permanently non-rotatably connected to the transmission output shaft 65a. The sixth coupling unit S6a is provided to connect the fourth ring gear P43a, the third planetary gear P43a. tenradträger P32a and the transmission output shaft 65a rotatably connect to each other. The coupling unit S6a has for the rotationally fixed connection of the rotatable coupling elements S61a, S62a only one Reibschlusseinheit 37a. The coupling unit S6a is designed as a multi-plate clutch. The friction-locking unit 37a comprises a disk pack for the rotationally fixed connection of the coupling elements S61a, S62a.

The second coupling unit S2a is combined (see Fig. 3). The second coupling unit S2a has a friction-locking unit 13a and a form-locking unit 14a connected in parallel to the friction-locking unit 13a in the force flow. The

Frictional engagement unit 13a and the parallel-connected form-fitting unit 14a are each provided to the rotatable coupling element S21 a of the second coupling unit S2a fixed to the housing and thus rotatably connected to the transmission housing 31 a. The second coupling unit S2a is assigned to the first planetary gear stage Pia. The Reibschlusseinheit 13 a and the form-fitting unit 14 a of the second coupling unit S2a are each operatively disposed between the rotatable coupling element S21 a and the gear housing 31 a.

The frictional engagement unit 13a of the combined coupling unit S2a is as one

Multi-disc brake formed. It is intended to frictionally connect the coupling elements S21 a, S22a. The friction-locking unit 13a comprises a plate pack for the rotationally fixed connection of the coupling elements S21a, S22a. The friction-locking unit 13a comprises first friction-locking elements 32a and second

Frictional engagement elements 33a. The first frictional engagement elements 32a are permanently non-rotatably connected to the rotatable coupling element S21a of the combined coupling unit S2a. The first frictional engagement elements 32a are formed as inner disks. The second frictional engagement elements 33a are permanently non-rotatably connected to the fixed coupling element S22a. They are thus permanently rotatable with the

Gear housing 31 a connected. In this case, the second frictional engagement elements 33a are arranged to be axially displaceable relative to the fixed coupling element S22a. The second frictional engagement elements 33a are designed as outer disks. Furthermore, the

Reibschlusseinheit 13a of the combined coupling unit S2a a

Outer plate carrier, which is permanently connected in rotation with the gear housing 31 a, and an inner disc carrier, the permanent rotationally fixed to the rotatable

Coupling element S21 a is connected to. The form-locking unit 14a of the combined coupling unit S2a is designed as a claw brake. It is intended to connect the coupling elements S21 a, S22a positively with each other. The form-locking unit 14a comprises a first positive-locking element 34a and a second positive-locking element 35a, which can be connected to one another in a form-fitting manner. The first positive locking element 34a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a of the combined coupling unit S2a. The first positive-locking element 34a s is permanently connected in a rotationally fixed manner to the inner disk carrier of the combined coupling unit S2a. The first friction engagement elements 32a of the friction engagement unit 13a and the first positive engagement element 34a of the positive engagement unit 14a are permanently connected to each other in a rotationally fixed manner. The second positive locking element 35a is permanently connected in a rotationally fixed manner to the fixed coupling element S22a. It is thus permanently rotatably connected to the transmission housing 31 a. The positive-locking elements 34a, 35a are arranged so as to be displaceable relative to one another along an axial actuating direction 36a. The second positive locking element 35a is disposed axially displaceable along the actuating direction 36a relative to the first positive locking element 34a and relative to the gear housing 31a. The second positive locking element 35a is rotatably, but axially displaceable with the fixed coupling element S22a and thus connected to the transmission housing 31 a. The actuation direction 36a is oriented parallel to the main rotation axis 66a. The first positive locking element 34a and the second positive locking element 35a each have a dog toothing for the positive connection, which are formed corresponding to one another. The dog teeth can be arranged radially or axially.

The Reibschlusseinheit 13 a and the form-fitting unit 14 a of the combined

Coupling unit S2a each have a design moment. The

The design moment of the friction engagement unit 13a and the design moment of the form-fitting unit 14a are different. The design moment of the

Friction unit 13a is smaller than the total design torque of the combined coupling unit S2a. The design moment of the form-fitting unit 14a corresponds to the total design moment of the combined coupling unit S2a. Thus, the design moment of the friction engagement unit 13a is smaller than the design moment of the form-fitting unit 14a. The form-fitting unit 14a is compared to

Reibschlusseinheit 13 a designed for the transmission of higher torque. The

Frictional engagement unit 13a of the combined coupling unit S2a has the lowest number of lamellae in comparison to the frictional engagement units 37a, 38a of the other coupling units S6a, S1a. The form-fitting unit 14a of the combined coupling unit S2a serves as a torque support for the Reibschlusseinheit 13 a of the combined

Coupling unit S2a.

FIG. 2 shows a circuit diagram of the transmission device. By doing

Schematic represents a black circle filled a closed and a missing black circle filled an open coupling unit S1 a, S2a, S3a, S4a, S5, S6a in the corresponding gear V1-V9, R dar. The formation of the

Forward gears V1-V9 and the reverse gear R by closing the coupling units S1 a-S6a is shown in the circuit diagram in Figure 2. A person skilled in the art will obtain from the circuit diagram in FIG. 2 in conjunction with the transmission diagram in FIG. 1 a power flow for each transmission gear.

The coupling unit S1 a is closed in the second forward gear V2, in the third forward gear V3, in the fifth forward gear V5 and in the sixth forward gear V6. The coupling unit S2a is in the eighth forward gear V8, in the ninth forward gear V9 and in the

Reverse gear R closed. The coupling unit S3a is closed in the first forward gear V1, in the second forward gear V2, in the sixth forward gear V6, in the seventh forward gear V7 and in the eighth forward gear V8. The coupling unit S4a is in the first forward gear V1, in the third forward gear V3, in the fourth forward gear V4, in the fifth forward gear V5, in the seventh forward gear V7, in the ninth forward gear V9 and in the

Reverse gear R closed. The coupling unit S5a is in the first forward gear V1, in the second forward gear V2, in the third forward gear V3, in the fourth forward gear V4 and in the

Reverse gear R closed. The coupling unit S6a is closed in the fourth forward gear V4, in the fifth forward gear V5, in the sixth forward gear V6, in the seventh forward gear V7, in the eighth forward gear V8 and in the ninth forward gear V9.

For actuating the friction-locking unit 13a of the combined coupling unit S2a and the form-fitting unit 14a of the combined coupling unit S2a, the

Transmission device two independent hydraulic actuators 15a, 16a on. The friction-locking unit 13a and the form-locking unit 14a are actuated in succession, wherein the friction-locking unit 13a engages in front of the form-locking unit 14a. The Form-fitting unit 14a is always closed with Reibschlusseinheit 13a

closed.

The first actuator 15a actuates the form-fitting unit 14a of the combined coupling unit S2 under pressure control. The first actuator 15a is disposed inside the transmission case 31a. The first actuator 15a is formed as a cylinder-piston unit. It has an actuating cylinder 39a, a piston element 40a and an actuating element 41a. The piston member 40a is arranged axially displaceable in the actuating cylinder 39a. The piston member 40a is fixedly connected to the actuator 41a. They are made in one piece with each other. The piston element 40a and the actuating element 41a are firmly connected to the second positive locking element 35a and axially displaceable, but non-rotatably connected to the fixed coupling element S22a and thus to the transmission housing 31a. The actuating cylinder 39a is fixedly connected to the transmission housing 31a. For positive connection of the coupling elements S21 a, S22a of the combined coupling unit S2a, the actuating element 41a of the first actuator 15a and thereby the second positive locking element 35a moves axially in the direction of the first positive locking element 34a until the correspondingly formed to each other dog teeth of the form-locking unit 14a engage in a form-fitting manner and the coupling elements S21a, S22a are positively connected with each other.

The first actuator 15a further includes a pressure chamber 42a. The pressure chamber 42a is provided for closing the form-fitting unit 14a. The first actuator 15a further includes another chamber in which a spring 44a is disposed. The piston member 40a separates the pressure chamber 42a and the other chamber fluidly from each other. The spring 44a is operatively disposed between the actuating cylinder 39a and the piston member 40a. A spring force of the spring 44a counteracts the force that can be generated by a hydraulic fluid pressure in the pressure chamber 42a. The hydraulic working fluid pressure acting in the pressure chamber 42a is formed as a jaw operating pressure provided for closing the form-fitting unit 14a. The spring 44a is formed as a spiral spring. Activation of the actuator 15a is provided for closing the form-locking unit 14a of the combined coupling unit S2a in the forward gears V8, V9 and in the reverse gear R.

The second actuator 16a actuates the friction-locking unit 13a of the combined coupling unit S2 under pressure control. The second actuator 16a is disposed inside the transmission case 31a. The second actuator 16a is analogous to the first actuator 15a, why the second actuator 16a is explained only briefly. The second actuator 16a has an actuating cylinder 45a, a piston element 46a and an actuator 47a. For the frictional connection of the coupling elements S21a, S22a of the combined coupling unit S2a, the actuating element 47a presses axially against the disk set of the friction-locking unit 13a, whereby the disks of the disk set move axially relative to each other until they abut each other and the coupling elements S21a, S22a are frictionally connected with each other. To close the

Frictional engagement unit 13a, the second actuator 16a, a pressure chamber 48a. In this case, the second actuator 16a has a spring 50a. An operating hydraulic pressure acting in the pressure chamber 48a is formed as a vane actuating pressure provided for closing the frictional engagement unit 13a. The pressure chamber 42a of the first actuator 15a and the pressure chamber 48a of the second actuator 16a are independent of each other with respect to an actuator supply. The pressure chamber 42a of the first actuator 15a and the pressure chamber 48a of the second actuator 16a are separated by printing technology. An activation of the actuator 16a is for

Closing the Reibschlusseinheit 13a of the combined coupling unit S2a provided in the forward gears V8, V9 and in the reverse gear R.

For actuating the coupling unit S6a, the transmission device has a third hydraulic actuator 21a (see FIG. 4). The third actuator 21a is within the

Gear housing 31a arranged. The third actuator 21a is analogous to the first actuator 15a, which is why the third actuator 21a is explained only briefly. The third actuator 21a has an actuating cylinder, a piston element and an actuating element. For closing the coupling unit S6a, the third actuator 21a has a pressure chamber 51a. An operating hydraulic pressure acting in the pressure chamber 51a is formed as a vane actuating pressure, which is used to close the

Reibschlusseinheit 37a is provided. An activation of the actuator 21a is for

Closing of the coupling unit S6a provided in the forward gears V4, V5, V6, V7, V8, V9.

For actuating the third coupling unit S1a, the transmission device has a fourth hydraulic actuator 26a. The fourth actuator 26a is within the

Gear housing 31a arranged. The fourth actuator 26a is analogous to the first actuator 15a, which is why the fourth actuator 26a is only briefly explained. The fourth actuator 26a has an actuating cylinder, a piston member and an actuator. For closing the coupling unit S1a, the fourth actuator 26a has a pressure chamber 52a. An operating hydraulic pressure acting in the pressure chamber 52a is called a blade actuating pressure is formed, which is provided for closing the Reibschlusseinheit 38 a. A drive of the actuator 26a is for

Closing of the coupling unit S1a provided in the forward gears V2, V3, V5, V6. In principle, the actuators 15a, 16a, 21a, 26a may also be designed pneumatically.

To set the operating medium pressure in the pressure chamber 42a of the first actuator 15a, the transmission device has a first solenoid valve 53a. The first solenoid valve 53a is provided to supply the power of the pressure chamber 42a of the first actuator 15a to build up the operating medium pressure in the pressure chamber 42a. The first solenoid valve 53a is provided for adjusting the jaw actuating pressure for closing the form-locking unit 14a. The first solenoid valve 53a has a

hydraulic equipment output 54a, which is pressure-related to the pressure chamber 42a of the first actuator 15a attachable. The first solenoid valve 53 a is as a

Regulated solenoid valve formed.

To set the operating medium pressure in the pressure chamber 48a of the second actuator 16a, the transmission device has a second solenoid valve, not shown. The second solenoid valve is provided for supplying the operating fluid to the pressure chamber 48a of the second actuator 16a for establishing the operating medium pressure in the pressure chamber 48a of the second actuator 16a. The second solenoid valve is for adjusting the

Slat actuation pressure for closing the Reibschlusseinheit 13 a provided. The second solenoid valve is connected by pressure to the pressure chamber 48a of the second actuator 16a. The second solenoid valve forms a second actuator 16a

Resource pressure source. The second solenoid valve is designed as a control solenoid valve.

For adjusting the operating medium pressure in the pressure chamber 51a of the third actuator 21a, the transmission device has a third solenoid valve (not shown). The third solenoid valve is provided to the operating medium supply of the pressure chamber 51 a of the third actuator 21 a for establishing the operating medium pressure in the pressure chamber 51 a of the third actuator 21 a. The third solenoid valve is provided for adjusting the vane actuation pressure to close the frictional engagement unit 37a. The third solenoid valve is connected by pressure to the pressure chamber 51a of the third actuator 21a. The third solenoid valve forms a resource pressure source for the third actuator 21a. The third solenoid valve is designed as a control solenoid valve. To set the operating medium pressure in the pressure chamber 52a of the fourth actuator 26a, the first solenoid valve 53a, which is also used to set the operating medium pressure in the pressure chamber 42a of the first actuator 15a, is used. The first solenoid valve 53a is also provided for supplying the pressure to the pressure chamber 52a of the fourth actuator 26a for establishing the operating medium pressure in the pressure chamber 52a of the fourth actuator 26a. The first solenoid valve 53a is for adjusting the

Slat actuation pressure for closing the Reibschlusseinheit 38 a of the third coupling unit S1 a provided. The first solenoid valve 53a is thus provided for adjusting the dog operating pressure in the pressure chamber 42a of the first actuator 15a and for adjusting the vane actuating pressure in the pressure chamber 52a of the fourth actuator 26a. The first solenoid valve 53 a has with respect to the setting of

Betriebsmitteldrucks a dual use, by which the first actuator 15a and the fourth actuator 26a can be supplied by the first solenoid valve 53a with the resource. The first solenoid valve 53a forms an operating medium pressure source for the first actuator 15a and for the fourth actuator 26a. Due to the double use is the

Positive locking unit 14a operated without an additional solenoid valve. For actuating the form-locking unit 14a and the three friction-locking units 13a, 37a, 38a, the transmission device has only three solenoid valves 53a. The solenoid valve 53a thus sets an operating medium pressure in the forward gears V2, V3, V5, V6, V8, V9 and in the reverse gear R, wherein the resource pressure in the

Forward gears V2, V3, V5, V6 as the vane actuation pressure to

Closing of the coupling unit S1 a and in the forward gears V8, V9 and in the reverse gear R is formed as the jaw operating pressure for closing the coupling unit S2a.

For controlling the double use of the first solenoid valve 53 a, the

Transmission device to a directional control valve 17a, which is provided for driving the first actuator 15a and for driving the fourth actuator 26a. The directional control valve 17a controls the resource supply of the pressure chamber 42a of the first actuator 15a and the resource supply to the pressure chamber 52a of the fourth actuator 26a. It is intended to selectively the pressure chamber 42 a of the first actuator 15 a and the

Pressure chamber 52a of the fourth actuator 26a to connect by pressure with the first solenoid valve 53a. In the forward gears V2, V3, V5, V6 connects the

Directional valve 17a provided for the coupling unit S1 a actuator 26a with the

Solenoid valve 53a and in the forward gears V8, V9 and in the

Reverse gear R the actuator provided for the coupling unit S2a 15a with the solenoid valve 53a. The directional control valve 17a has a first hydraulic working line connection 28a, a second hydraulic working line connection 29a, a hydraulic

Supply line connection 55a and a hydraulic drain port 56a. The first working line connection 28a is connected by pressure to the first actuator 15a provided for actuating the form-locking unit 14a. The first

Working line connection 28a is connected by pressure to a hydraulic working line 57a of the transmission device, which opens into the pressure chamber 42a of the first actuator 15a. The working line 57a connects the pressure chamber 42a of the first actuator 15a and the first working line connection 28a of the directional control valve 17a to one another by means of printing technology. The second working line connection 29a is by printing technology to the fourth actuator 26a provided for actuating the third coupling unit S1a

tethered. The second working line connection 29a is connected by pressure to a hydraulic working line 58a of the transmission device, which opens into the pressure chamber 52a of the fourth actuator 26a. The working line 58a connects the

Pressure chamber 52a of the fourth actuator 26a and the second working line port 29a of the directional control valve 17a with each other by printing technology. The working lines 57a, 58a are separated by printing technology.

The supply line connection 55a is connected by pressure to the first solenoid valve 53a. The supply line connection 55a is connected by pressure to a hydraulic supply line 59a of the transmission device, which is connected by pressure to the first magnetic valve 53a. The supply line 59a connects the resource outlet 54a of the first solenoid valve 53a and the

Supply line connection 55 a of the directional control valve 17 a printing technology together. In the supply line 59a and thus at the supply line connection 55a, at least substantially the operating medium pressure set by the first magnetic valve 53a prevails. The first solenoid valve 53a can be connected to the first actuator 15a and the fourth actuator 26a by means of the directional control valve 17a and selectively separable from these. The drain connection 56a opens into a pressureless resource reservoir.

For hydraulic control, the directional control valve 17a has three hydraulic

Control line terminals 18a, 19a, 20a. The first control line connection 18a is provided for the hydraulic actuation of the directional control valve 17a into a valve position, in which the first actuator 15a is connected by pressure to the first magnetic valve 53a. The first control line connection 18a of the directional control valve 17a is permanently in the form of a pressure provided with the second one provided for actuating the friction-locking unit 13a Actuator 16a connected. The first control line connection 18a of the directional control valve 17a is permanently connected to the pressure chamber 48a of the pressure for actuating the

Friction unit 13a provided second actuator 16a connected. A

Control pressure tapping point for the control line connection 18a is located on the directional valve 17a facing side of the filler panel 70a. At the first

Control line terminal 18a of the directional control valve 17a is in the forward gears V8, V9 and in the reverse gear R, the lamellae operating pressure, which is provided for closing the Reibschlusseinheit 13a. In the

Forward gears V1, V2, V3, V4, V5, V6, V7, the first control line terminal 18a of the directional control valve 17a at least substantially unpressurized.

The second control line port 19a is for hydraulic actuation of the

Directional valve 17a provided in the valve position, in which the first actuator 5a

pressure-technically connected to the first solenoid valve 53a. The second

Control line connection 19a of the directional control valve 17a is permanently connected by pressure to the first actuator 15a provided for actuating the form-locking unit 14a. The second control line connection 19a of the directional control valve 17a is permanently connected by pressure to the pressure chamber 42a of the first actuator 15a provided for actuating the form-fitting unit 14a. The second control line connection 19a of the directional control valve 17a is provided to maintain the valve position, in which the first actuator 15a is connected by pressure to the first solenoid valve 53a. In a state where the first actuator 15a is connected to the first solenoid valve 53a, at least substantially the operating medium pressure set by the first solenoid valve 53a is applied to the second control line port 19a of the directional control valve 17a. Advantageously, due to the filler panel 67a, an operating medium pressure on

Control line terminal 19a in a release operation of a tooth-on-tooth position of the form-locking unit 14a at the moment in which the operating medium pressure in the

Pressure chamber 42 a of the first actuator 15 a decreases, wherein a drop in the

Betriebsmitteldrucks in the pressure chamber 42 a by snapping the

Forming element 34a and 35a of the form-locking unit 14a and thereby caused slipping of the actuating element 40a of the actuator 15a is effected, not so strong with from that the directional control valve 17a switches to a connection of the solenoid valve 53a with the coupling unit S1 a. At the second control line connection 19a of the directional control valve 17a is in the forward gears V8, V9 and in the

Reverse gear R, the claw actuation pressure, which is provided for closing the form-locking unit 14a. The first control line connection 18a and the second control line connection 19a of the directional control valve 17a are printing technology separated from each other. In the forward gears V1, V2, V3, V4, V5, V6, V7, the second control line connection 19a of the directional control valve 17a is at least substantially free of pressure.

The third control line connection 20a is provided for the hydraulic actuation of the directional control valve 17a into a valve position in which the first actuator 15a is pressure-separated from the first magnetic valve 53a. The third control line terminal 20a of the

Directional control valve 17a is permanent printing technology with the to actuate the

Coupling unit S6a provided third actuator 21 a connected. The third

Control line connection 20a of the directional control valve 17a is permanently connected by pressure to the actuator 21a, which is provided to actuate the forward gearshifts V4, V5, V6, V7, V8, V9 provided for coupling unit S6a. The third

Control line connection 20a of the directional control valve 17a is permanently connected by pressure to the pressure chamber 51a of the third actuator 21a provided for actuating the friction-locking unit 37a. At the third control line connection 20a of the directional control valve 17a is at least substantially in the pressure chamber 51 a of the third actuator 21 a prevailing operating medium pressure. At the third control line connection 20a of the directional control valve 17a, in the forward gears V4, V5, V6, V7, V8, V9, there is at least substantially the vane actuation pressure which is used to close the

Reibschlusseinheit 37a is provided. The first control line connection 18a, the second control line connection 19a and the third control line connection 20a of the directional control valve 17a are each separated from each other by printing technology. In the

Forward gears V1, V2, V3 and in the reverse gear R, the third control line connection 20a of the directional control valve 17a at least substantially unpressurized.

For hydraulic actuation, the directional control valve 17a has a first control volume, a second control volume and a third control volume. The first

Control line terminal 18a is the first control volume, the second

Control line terminal 19a the second control volume and the third

Control line connection 20a associated with the third control volume. The first

Control volume is supplied by the first control line terminal 18a with the resource. In the first control volume prevails at least substantially in the pressure chamber 48a of the second actuator 16a prevailing operating medium pressure. In the first control volume prevails in the forward gears V8, V9 and in the reverse gear R, at least substantially the vane actuation pressure, which is provided for closing the Reibschlusseinheit 13a. The second control volume can be supplied with the operating means by the second control line connection 19a. In the second control volume prevails at least substantially in the

Pressure chamber 42 a of the first actuator 15 a prevailing operating medium pressure. In the second control volume prevails in the forward gears V8, V9 and in the reverse gear R at least substantially the jaw operating pressure, which is provided for closing the form-locking unit 14a. The third control volume can be supplied with the operating means by the third control line connection 20a. In the third control volume prevails at least substantially in the pressure chamber 51 a of the third actuator 16 a prevailing operating medium pressure. In the third control volume prevails in the forward gears V4, V5, V6, V7, V8, V9 at least in

Essentially the vane actuation pressure provided for closing the frictional engagement unit 37a. The control volumes of the directional valve 17a are each separated by printing technology.

For printing connection of the control line connections 18a, 19a, 20a, the transmission device has three control lines 60a, 61a, 62a. The first control line 60a connects the first control line terminal 18a and the second actuator 16a

printing technology together. The first control line 60a supplies the first one

Control volume of the directional control valve 17a with the operating medium from the pressure chamber 48a of the second actuator 16a. The second control line 61 a connects the second

Control line connection 9a and the first actuator 15a printing technology together. The second control line 61 a supplies the second control volume of the directional control valve 17 a with the operating means provided by the first solenoid valve 53 a. The second

Control line 61 connects a pressure technically the second control volume of the directional control valve 17a with the working line 57a, which connects the first working line connection 28a with the first actuator 15a. The third control line 62a connects the third

Control line connection 20a and the third actuator 21 a printing technology together. The third control line 62a supplies the third control volume of the directional control valve 17a with the operating medium from the pressure chamber 51a of the third actuator 21a.

The first control line terminal 18a and the second control line terminal 19a are provided for operating the directional control valve 17a in a same direction. They are provided for setting the same valve position of the directional valve 17a. A force prevailing in the first control volume and a force prevailing in the second control volume are provided for setting the same valve position of the directional control valve 17a. The first control volume and the second control volume are each by a

Limited control, which act in the direction of the same valve position. The first control surface associated with the first control line connection 18a, ie, the first control surface Control volume limiting control surface and the second control line 19a associated second control surface, ie the second control volume limiting control surface are oriented in the same direction.

The third control line terminal 20a is compared to the first one

Control line terminal 18a and the second control line terminal 19a to

Operation of the directional control valve 17 a provided in an opposite direction. The third control line connection 20a is provided in comparison to the control line connections 18a, 19a for setting an opposite valve position of the directional control valve 17a. A force prevailing in the third control volume is compared to the force prevailing in the first control volume and to that in the second control volume

Control volume prevailing force to adjust an opposite

Valve position of the directional control valve 17 a provided. The force prevailing in the third control volume counteracts the force prevailing in the first control volume and the force prevailing in the second control volume. The third control volume is limited by a third control surface, the first control surface bounding the first control volume and the second control volume limiting second

Control surface acts in an opposite valve position. The third

Control line terminal 20a associated third control surface, i. the third

Control volume limiting control surface is opposite to the first control line terminal 18 a associated first control surface and to the second control line terminal 19 a associated second control surface oppositely oriented. The slat actuation pressure provided for closing the combined coupling unit S2a, the claw actuation pressure provided for closing the combined coupling unit S2a, and the slipping actuation pressure provided for closing the coupling unit S6a

Slat actuation pressure in each case act as control pressure in the directional control valve 17a, wherein the slat actuation pressure provided for closing the coupling unit S6a is provided for closing the combined coupling unit S2a

Slat actuation pressure and the claw actuation pressure provided for closing the combined coupling unit S2a counteracts.

The directional control valve 17a further has a spring 24a which, in terms of its operation, is directed counter to the first control line connection 18a and the second control line connection 19a and is rectified to the third control line connection 20a. The spring 24a counteracts the force prevailing in the first control volume and the force prevailing in the second control volume. The spring 24a acts in the direction of the force prevailing in the third control volume. The spring 24a is to provided to be biased by the force prevailing in the first control volume. It is biased by the louver actuation pressure provided to close the frictional engagement unit 13a. The spring 24a is intended to remain biased by the force prevailing in the second control volume. The spring 24a has a spring force which is rectified with respect to a switching direction to the third control surface. The spring force of the spring 24a is opposite in direction to the first control surface and the second control surface. The spring force of the spring 24a and provided for closing the coupling unit S6a

Vane actuation pressures counteract the vane actuation pressure provided to close the combined coupling unit S2a and the jaw actuation pressure provided to close the combined coupling unit S2a. The spring 24a is formed as a spiral spring. The directional control valve 17a is designed as a 4/2-way valve.

The directional control valve 17a is formed as a slide valve. It has a valve slide on which the operating medium pressure acts in the control volumes of the directional control valve 17a. The valve spool of the directional control valve 17a has the control surfaces. The Indian

Pressure chamber 42a of the first actuator 15a prevailing operating medium pressure and prevailing in the pressure chamber 48a of the second actuator 16a operating medium pressure act in the same direction of movement on the valve spool of the directional control valve 17a. The operating pressure prevailing in the pressure chamber 51a of the third actuator 21a and the spring force of the spring 24a act on the valve spool of the directional control valve 17a in the same direction of movement. In this case, the prevailing in the pressure chamber 42a of the first actuator 15a operating medium pressure and prevailing in the pressure chamber 48a of the second actuator 16a operating medium pressure in the pressure chamber 51 a of the third actuator 21 a prevailing operating medium pressure and the spring force of the spring 24a counter. The provided for closing the Reibschlusseinheit 13 a

Slat actuation pressure and the closing of the form-locking unit 14a

provided claw actuation pressure act on the valve spool to adjust the valve position, in which the first actuator 15a is connected by pressure to the first solenoid valve 53a. The provided for closing the Reibschlusseinheit 37 a

Slat actuation pressure and the spring force of the spring 24a act on the

Valve slide for adjusting the valve position, in which the first actuator 15a

is technically separated from the first solenoid valve 53a. The spring force of the spring 24a and provided for closing the coupling unit S6a

Slat actuation pressure act against closing the combined

Coupling S2a provided slat actuation pressure and against the Closing the combined coupling unit S2a provided claw operation pressure on the valve spool of the directional control valve 17a.

To a defined time behavior and / or a defined response to the

adjust appropriate equipment pressure, the transmission device has a plurality of filling nozzles 67a, 68a, 69a, 70a. The filling nozzle 67a is arranged fluidically between the pressure chamber 42a of the actuator 15a and the directional control valve 17a. The

Filling nozzle 67a is arranged in the working line 57a. The filling nozzle 68a is

fluidically between the pressure chamber 52a of the actuator 26a and the

Directional valve 17 a arranged. The filling nozzle 68a is arranged in the working line 58a. The filling nozzle 69 a is fluidically arranged between the pressure chamber 51 a of the actuator 26 a and the directional control valve 17 a. The filling nozzle 70a is arranged fluidically between the pressure chamber 48a of the actuator 16a and the directional control valve 17a. The Befülldüsen 67 a, 68 a, 69 a, 70 a are each formed as a Befüllblende.

In principle, at least one of the filling nozzles 67a, 68a, 69a, 70a can be dispensed with.

The directional control valve 17a has a first Ventilsteliung, in which its second

Working line connection 29a is connected to its supply line connection 55a, and a second valve position, in which its first working line connection 28a is connected to the supply line connection 55a, on. In the first valve position of the directional control valve 17a are its second working line connection 29a with his

Supply line connection 55a and its first working line connection 28a connected to its outlet connection 56a. In the second valve position of the directional control valve 17 a, its first working line connection 28 a with its

Supply line port 55a and its second working line port 29a connected to its drain port 56a. In the first valve position of the directional control valve 17 a, the first solenoid valve 53 a with the pressure for the actuation of

Coupling unit S1 a provided actuator 26a connected. In the second valve position of the directional control valve 17 a, the first solenoid valve 53 a with the pressure to the

Actuation of the form-locking unit 14a of the combined coupling unit S2a provided actuator 15a connected. In the forward gears V1, V2, V3, V4, V5, V6, V7, the directional control valve 17a is switched in its first valve position. In the

Forward gears V8, V9 and in the reverse gear R is the

Directional valve 17a connected in its second valve position. The directional control valve 17a switches to its first valve position when a sum of a force acting on the valve spool, which provided by the closing of the coupling unit S6a Slat actuation pressure results, and the force acting on the valve spool spring force of the spring 24a is greater than a sum of a force acting on the valve spool, which provided by the closing of the coupling unit S2a

Slat actuation pressure results, and a force acting on the valve spool, which provided by the closing of the coupling unit S2a

Claw actuation pressure results. The directional control valve 17a switches to its second

Valve position when the sum of the force acting on the valve spool, which provided by the closing of the coupling unit S6a

Slat actuation pressure results, and the force acting on the valve spool spring force of the spring 24a is smaller than the force acting on the valve spool, resulting from the provided for closing the coupling unit S2a slat actuation pressure. In the figure 4, the directional control valve 17a is shown in the first valve position.

The first valve position of the directional control valve 17a is formed as a basic position, which automatically adjusts itself in a pressureless state of the pressure chambers 42a, 48a, 51a. For this purpose, the directional control valve 17a on the spring 24a. The spring 24a independently adjusts the first valve position in the forward gears V1, V2, V3. In its first valve position, the directional control valve 17 a connects the first solenoid valve 53 a with the fourth actuator 26 a, whereby the pressure chamber 52 a of the fourth actuator 26 a with the set by the first solenoid valve 53 a operating medium pressure to close the

Coupling unit S1 a can be acted upon. In its second valve position, the directional control valve 17a connects the first solenoid valve 53a with the first actuator 15a, whereby the pressure chamber 42a of the first actuator 15a with the first through the first

Solenoid valve 53a set operating medium pressure for closing the form-locking unit 14a of the combined coupling unit S2a can be acted upon.

The second valve position of the directional control valve 17a is formed as a switching position, which is adjusted by pressure. For switching the directional control valve 17a in the second

Valve position is increased by means of the second solenoid valve, the operating pressure in the pressure chamber 48a until the force resulting from the operating medium pressure in the first control volume of the directional control valve 17a exceeds the spring force of the spring 24a and the force resulting from the operating medium pressure in the third control volume. The directional control valve 17a shifts to the second valve position when the force resulting from closing the frictional engagement unit 13a in the first control volume is greater than the sum of the spring force of the spring 24a and that for closing the frictional engagement unit 37a

provided slat actuation pressure resulting force in the third Control volume. As a result, the directional control valve 17a connects the first actuator 15a and the first solenoid valve 53a to one another by means of printing technology, whereby the positive locking unit 14a of the combined coupling unit S2a can be closed. When closing the form-locking unit 14a is a tooth-on-tooth position between the

Positive locking elements 34a, 35a before, a slip state between the

Frictional engagement elements 32a, 33a of the Reibschlusseinheit 13a set by a reduction of the lamellae actuation pressure in the pressure chamber 48a, whereby the tooth-on-tooth position is resolved. The lamella actuation pressure in the pressure chamber 48a is reduced only so far, so that the sum of the force in the first

Control volume and the force in the second control volume is greater than the sum of the force in the third control volume and the spring force, whereby the

closed state of the form-locking unit 14a is maintained. In order to open the form-fitting unit 4a again, the pressure via the solenoid valve 53a is first reduced. Only then, to release the solenoid valve 53a and to connect to the switching element S1 a, the position of the directional control valve is switched. For this purpose, the operating medium pressure in the pressure chamber 48a of the second actuator 16a is lowered and / or the operating medium pressure in the pressure chamber 51a of the third actuator 21a is increased until the sum of the spring force of the spring 24a and the force resulting from the operating medium pressure in the third control volume Sum of the by the

Operating fluid pressure in the first control volume resulting force and the force resulting from the operating medium pressure in the second control volume exceeds force. The switching of the directional control valve 17 a can also be done only by raising the pressure in the pressure chamber 51 a at a constant pressure in the pressure chamber 48 a. The directional control valve 17a switches to its first valve position when the sum of the force in the third control volume and the spring force is greater than the sum of the force in the first control volume and the force in the second control volume. As a result, the third coupling unit S1 a can again be closed by means of the first solenoid valve 53 a.

To close the form-fitting unit 14a of the combined coupling unit S2a, the force resulting from the operating medium pressure in the pressure chamber 48a of the second actuator 16a on the valve spool must be greater than the sum of the spring force of the spring 24a and that of the operating medium pressure in the pressure chamber 51 a of the third Actuator 21 a resulting force on the valve spool, whereby the directional control valve 17a switches to its second valve position. Furthermore, the first solenoid valve 53 must provide an operating medium pressure by which the form-fitting unit 14a is closed. In the forward gears V1, V2, V3, V4, V5, V6, V7, the vane actuation pressure provided for closing the combined clutch S2a is zero, whereby in the forward gears V1, V2, V3 the spring force of the spring 24a and in the forward gears V4, V5, V6, V7 of the lamination actuating pressure provided for closing the coupling unit S6a moves the valve spool of the directional control valve 17a into the first valve position. In the forward gears V8, V9 is the force acting on the valve spool, which by closing the combined

Coupling unit S2a provided lamination actuation pressure results, greater than the sum of the force acting on the valve spool spring force of the spring 24a and the force acting on the valve spool, which results from the closing of the coupling unit S6a slat actuation pressure, whereby the closing operation of the combined coupling unit S2a provided slat actuation pressure moves the valve spool of the directional control valve 17a in the second valve position. In the

Forward gears V8, V9 must be the one to close the combined

Coupling unit S2a provided louver actuation pressure to move the valve spool against the provided for closing the coupling unit S6a lamination actuation pressure and against the spring force of the spring 24a. In the reverse gear, the force acting on the valve spool resulting from the vane actuating pressure provided to close the combined clutch unit S2a is greater than the spring force of the spring 24a acting on the spool valve, whereby the vane actuating pressure provided for closing the combined clutch unit S2a is the spool valve of the directional control valve 17a moves to the second valve position. By doing

Reverse gear R, the louver actuation pressure provided to close the combined clutch unit S2a must move the valve spool only against the spring force of the spring 24a, since the louver actuation pressure in the reverse gear R provided for closing the clutch unit S6a is zero.

If provided for closing the combined coupling unit S2a

Slat actuation pressure in the forward shifts geared V8, V9 and in the reverse gear R drops, in particular for dissolving a tooth-on-tooth position in the form-fitting unit 14a of the combined coupling unit S2a, holding the sum of the provided for closing the combined coupling unit S2a jaw operating pressure and to a pressure level below a holding pressure for the fins of the Reibschlusseinheit 13a lowered lamellar actuation pressure the

Valve spool of the directional control valve 17a in the second valve position, since the sum of these forces acting on the valve spool forces is greater than the sum of the on the Valve slide oppositely acting spring force of the spring 24a and the force provided for closing the coupling unit S6a

Slat actuation pressure results.

The embodiment of the invention shown in FIG. 4 advantageously makes it possible to release a tooth-on-tooth position of the form-fit unit 14a at a low level

mechanical load on the dog teeth. The mechanical load of the dog teeth when releasing a tooth-on-tooth position can be kept low with the embodiment shown in Fig. 4, since the jaw actuating pressure only greater than the sum of the forces from the operating pressure of

Coupling unit S6a and the spring force of the spring 24a must be. In addition, in the embodiment, by providing two control surfaces, the first control surface and the second control surface, which are respectively associated with the first control line terminal 19a and the second control line terminal 20a

Invention, which is shown in Fig. 4, when dissolving a tooth-on-tooth position, a residual operation pressure, such as the pressure level of the return spring of the parallel Reibschlusseinheit 13 a, to obtain at the directional control valve 17 a, which together with the jaw operating pressure, the valve pitch of Directional valve 17a holds when releasing a tooth-on-tooth position. The jaw actuation pressure when releasing a tooth-on-tooth position can therefore be set lower.

The claw actuation pressure is advantageously smaller than a working pressure of

Transmission device. In the reverse gear R advantageously the third actuator is not acted upon by actuating pressure, so that in the reverse gear R no

Compressive force applied to the third control line terminal 20a. The claw actuation pressure exerts an axial force on the dog teeth. The higher the axial force on the

Claw toothing is, the higher is a wear of the dog teeth in a release operation of a tooth-on-tooth position of the dog teeth.

Further, due to the comparatively small claw actuating pressure required to release a tooth-on-tooth position, the diameter of the filling nozzle 67a

be formed comparatively large, which in the embodiment of the invention shown in Fig. 4, the diameter of the filling nozzle 67a does not delay in a Auslegevorgang the form-locking unit 14a, so that advantageously a spontaneous interpretation of the form-locking unit 14a is possible. FIGS. 5 and 6 show two further exemplary embodiments of the invention. The following description is essentially limited to the differences between the exemplary embodiments, with reference in principle also to the figure and / or figures and / or the description of the other with respect to the same components, in particular with respect to components having the same reference numerals

Embodiments, in particular of the embodiment in Figures 1 to 4, can be referenced. To distinguish the embodiments, the letter a in the reference numerals of the embodiment in Figures 1 to 4 by the letter b and c in the reference numerals of the embodiments in Figures 5 and 6 is replaced.

FIG. 5 partially shows a transmission device for a motor vehicle in a second exemplary embodiment. The transmission device comprises a combined coupling unit S2b which has a friction-locking unit 13b and a locking unit 14b connected in parallel to the friction-locking unit 13b, a first hydraulic actuator 15b for actuating the form-locking unit 14b, a second hydraulic actuator 16b for actuating the friction-locking unit 13b, and for the non-rotatable connection of two coupling elements a directional control valve 17b provided for driving the first actuator 15b, which has a first control line connection 18b, a second control line connection 19b and a third control line connection 20b. The first control line connection 18b is printing technology with the second actuator 16b and the second

Control line connection 19b pressure-technically connected to the first actuator 15b. Furthermore, the directional control valve 7b has a first working line connection 28b, which is connected to the first actuator 15b of the combined coupling unit S2b, and a second working line connection 29b, which is connected to a fourth actuator 26b for actuating a further coupling unit S1b. The directional control valve 17b further includes a spring 25b. For supplying the first actuator 15b and the fourth actuator 26b with operating medium, the transmission device has a first magnetic valve 53b. The directional control valve 17b controls the double use of the first solenoid valve 53b. The transmission device further has a working pressure system 23b, in which a working pressure prevails.

In contrast to the previous embodiment, the third

Control line connection 20b permanently connected by pressure to the working pressure system 23b. At least substantially the working pressure is applied to the third control line connection 20b of the directional control valve 17b. Thus prevails in a third

Control volume of the directional control valve 17b, the working pressure. The working pressure acts on an operating medium pressure applied to the first control line connection 18b and on opposite to the second control line connection 19b operating medium pressure. One provided for closing the combined coupling unit S2b

Slat actuation pressure, a claw actuation pressure provided to close the combined coupling unit S2b, and the working pressure each act as

Control pressure in the directional control valve 17b, wherein the working pressure provided to the closing of the combined coupling unit S2b slat actuation pressure and to close the combined coupling unit S2b

Counteracts claw actuation pressure. The working pressure acts on a valve spool of the directional control valve 17b to set a valve position, in which the first actuator 15b is separated by pressure from the first solenoid valve 53b.

In a further difference from the previous exemplary embodiment, the spring 25b is in terms of its operation directed counter to the third control line connection 20b and rectified to the first control line connection 18b and the second control line connection 19b. The spring 25b acts counter to a force prevailing in a third control volume of the directional valve 17b force on the valve spool. The spring 25b acts in the direction of a force prevailing in a first control volume of the directional control valve 17b and in the direction of a second control volume of the directional control valve 17b

prevailing force on the valve spool. The spring 25b is intended to be biased by the force prevailing in the third control volume. It is biased by the working pressure. The spring 25b acts on the valve spool of the directional control valve 17b to set a valve position, in which the first actuator 15b is connected by pressure to the first solenoid valve 53b. The spring 25b has a spring force with respect to a switching direction to the third control surface

is opposite. The spring force of the spring 25b is rectified with respect to the switching direction to a first control surface of the directional control valve 17b and to a second control surface of the directional control valve 17b. The spring force of the spring 25b cooperates with that provided for closing the combined coupling unit S2b

Slat actuation pressure and provided for closing the combined coupling unit S2b claw operation pressure against the working pressure.

Further, a jaw operating pressure set by the first solenoid valve 53b in a pressure chamber 42b of the first actuator 15b and the working pressure are at least substantially equal to the previous embodiment. In addition, the lamella actuation pressure set by a second solenoid valve is in one

Pressure chamber 48b of the second actuator 16b and the working pressure, in contrast to the previous embodiment, at least substantially equal. The directional control valve 17b has a first valve position, in which its first

Working line port 28b is connected to its supply line connection 55b, and a second valve position, in which its second working line connection 29b is connected to the supply line connection 55b, on. In the first valve position of the directional control valve 17b are its first working line connection 28b with his

Supply line terminal 55b and its second working line port 29b connected to its drain port 56b. In the second valve position of the directional control valve 17b are its second working line connection 29b with his

Supply line terminal 55b and its first working line port 28b connected to its drain port 56b. In the first valve position of the directional control valve 17 b, the first solenoid valve 53 b is connected by pressure to the first actuator 15 b, whereby the pressure chamber 42 a of the first actuator 15 b with the first

Solenoid valve 53b set jaw operating pressure to close the

Form-fitting unit 14b can be acted upon. In the second valve position of the directional control valve 17b, the first solenoid valve 53b is connected by pressure to the fourth actuator 26b, whereby a pressure chamber 52b of the fourth actuator 26b can be acted upon by a louver actuation pressure set by the first solenoid valve 53b to close the coupling unit S1b. In the figure 5, the directional control valve 17b is shown in the first valve position. The first valve position of the directional control valve 17b adjusts itself in the case of a pressureless working pressure system 23b. This points to that

Directional control valve 17b on the spring 25b. In the presence of a working pressure and pressure-less pressure chambers 42b, 48b, the directional control valve 17b is switched in its second valve position. Since the working pressure and the lamella actuation pressure provided for closing the frictional engagement unit 13b in the pressure chamber 48b at least in the

Are substantially the same, the directional control valve 17b switches due to the spring 25b in its first valve position when prevails in the pressure chamber 48b of the louver actuation pressure.

To switch the directional control valve 17b from the second valve position to the first valve position, the second solenoid valve closes the valve

Frictional engagement unit 13b provided slat actuation pressure in the pressure chamber 48a of the second actuator 16b set. The spring 25b adjusts the first valve position when the louver actuation pressure for closing the frictional engagement unit 13b is set in the pressure chamber 48b. In order to reopen the form-locking unit 14a, a pressure reduction initially takes place via the magnetic valve 53b. Only then is the position of the directional control valve 17b changed, so that via the solenoid valve 53b the Switching element 27b can be controlled again. The slide switch only changes its switching position when the force on the directional control valve through the

Slat actuation pressure in the pressure chamber 48b together with the spring force is smaller than the force on the directional control valve by the working pressure. This can be achieved by the working pressure is controlled higher than the

Slat actuation pressure in the pressure chamber 48b.

In the forward gears V1, V2, V3, V4, V5, V6, V7, the louver actuation pressure provided to close the combined clutch S2b is zero, whereby the working pressure shifts the valve spool of the directional control valve 17b to the second

Valve position moves because the force acting on the valve spool, resulting from the working pressure, is greater than the spring force of the spring 24b. In the

For forward gears V1, V2, V3, V4, V5, V6, V7, the working pressure must be

Move valve spool only against the spring force of the spring 24b. In the

Forward gears V8, V9 and the reverse gear R are the force acting on the valve spool, which by closing the combined

Coupling unit S2b slat actuation pressure results, and the force acting on the valve spool, resulting from the working pressure, the same size, whereby the spring force of the spring 24b moves the valve spool of the directional control valve 17b in the first valve position.

To a defined time behavior and / or a defined response to the

Adjusting the appropriate fluid pressure, the transmission device shown in Fig. 5, at least the filling nozzle 67 b. The filling nozzle 67b is

fluidically between the pressure chamber 42b of the actuator 15b and the

Directional valve 17b arranged.

FIG. 6 partially shows a transmission device for a motor vehicle in a third exemplary embodiment. The transmission device comprises a combined coupling unit S2c, which has a friction-locking unit 13c and a form-locking unit 14c connected in parallel to the friction-locking unit 13c, a first hydraulic actuator 15c for actuating the form-locking unit 14c, a second hydraulic actuator 16c for actuating the friction-locking unit 13c and 13c, for the rotationally fixed connection of two coupling elements a directional control valve 17c provided for driving the first actuator 15c. Further, the directional control valve 17c has a first working pipe port 28c connected to the first actuator 15c of the combined coupling unit S2c, and a second working pipe port 29c provided with a fourth actuator 26c for operation a second further coupling unit Si c is connected to. The directional control valve 17c further includes a spring 25c. For supplying the first actuator 15c and the fourth actuator 26c with operating medium, the transmission device has a first magnetic valve 53c. The directional control valve 17c controls the double use of the first solenoid valve 53c. The

Transmission device further includes a working pressure system 23c. Further, a jaw operating pressure set by the first solenoid valve 53c corresponds to one

Pressure chamber 42c of the first actuator 15c and a set by a second solenoid valve actuation pressure in a pressure chamber 48c of the second actuator 16c a working pressure in the working pressure system 23c.

In contrast to the previous exemplary embodiment, the directional control valve 17b has only two control line connections 18c, 20c and thus only two control volumes. The first control line connection 18c can be connected to the first actuator 15c and the second actuator 16c by printing technology. For pressure-dependent connection of the first control line connection 18c to the first actuator 15c or to the second actuator 16c, the transmission device has a change-over valve 30c. The switching valve 30c connects the first control line port 18c to the first actuator 15c when a jaw actuation pressure in the pressure chamber 42c of the first actuator 15c is greater than a louver actuation pressure in the pressure chamber 48c of the second actuator 16c. The

Change-over valve 30c connects the first control line port 18c to the second actuator 16c when the vane-actuating pressure in the pressure chamber 48c is greater than the jaw-actuating pressure in the pressure chamber 42c. The changeover valve 30c is formed as a ball switching valve.

The other control line connection 20c is permanently printing technology with the

Working pressure system 23c connected. The working pressure and an operating medium pressure at the first control line port 18c act against each other on a valve spool of the directional control valve 17c. An associated with the first control line terminal 18c

Control surface of the valve spool and a control surface of the valve spool associated with the other control line connection 20c are oriented opposite to one another. A spring force of the spring 25c is opposite to the third control line terminal 20c and rectified to the first control line terminal 18c. The spring 25c acts counter to a force prevailing in a third control volume of the directional control valve 17c force on the valve spool.

To a defined time behavior and / or a defined response to the

adjust appropriate equipment pressure, the transmission device, which in 6, at least the filling nozzle 67c. The filling nozzle 67c is

fluidically arranged between the pressure chamber 42c of the actuator 15c and the directional control valve 17c.

LIST OF REFERENCE NUMBERS

Reibschlusseinheit

Form-fitting unit

actuator

way valve

Control line connection

actuator

Working pressure system

feather

actuator

Working line connection

switching valve

gearbox

frictional engagement

Form-fitting element

operating direction

Reibschlusseinheit

actuating cylinder

piston element

actuator

pressure chamber 4 spring

5 actuating cylinders

6 piston element

7 actuator

8 pressure chamber

0 spring

1 pressure chamber

2 pressure chamber

3 solenoid valve

4 Equipment outlet 5 Supply pipe connection 6 Drain connection

7 work management

8 work management

9 supply line

0 control line

1 control line

2 control line

63 Gearset

64 transmission input shaft

65 Transmission output shaft

66 main axis of rotation

67 filling nozzle

68 filling nozzle

69 filling nozzle

70 filling nozzle

P1 planetary gear

P11 sun wheel

P12 planet carrier

P13 ring gear

P14 planetary gear

P2 planetary gear

P21 sun wheel

P22 planet carrier

P23 ring gear

P24 planetary gear

P3 planetary gear P31 sun wheel

P32 planet carrier

P33 ring gear

P34 planetary gear

P4 planetary gear

P41 sun wheel

P42 planet carrier

P43 ring gear

P44 planetary gear

51 coupling unit

51 1 coupling element

512 coupling element

52 coupling unit

521 coupling element

522 coupling element

53 coupling unit

531 coupling element

532 coupling element

54 coupling unit

541 coupling element

542 coupling element

55 coupling unit

551 coupling element

552 coupling element

56 coupling unit

561 coupling element

562 Coupling element V1 Forward gear V2 Forward gear V3 Forward gear V4 Forward gear V5 Forward gear V6 Forward gear V7 Forward gear V8 Forward gear V9 Forward gear R Reverse gear

Claims

claims

Transmission device for a motor vehicle, comprising at least one coupling unit (S2a; S2b; S2c) which, for the rotationally fixed connection of two coupling elements (S21a, S22a), has a friction-locking unit (13a, 13b; 13c) and a parallel to

With a first hydraulic and / or pneumatic actuator (15a, 15b, 15c) for actuating the form-locking unit (14a, 14b, 14c), with a second hydraulic drive unit (14a, 14b, 14c) hydraulic and / or pneumatic actuator (16a; 16b; 16c) for actuating the friction-locking unit (13a; 13b; 13c) and with a directional control valve (17a; 17b; 17c) for controlling the actuating unit (14a; 14b; 14c) to be actuated first actuator (15a, 15b, 15c),

characterized in that

the directional control valve (17a; 17b; 17c) has a control line connection (18a; 18b; 18c) which, in at least one operating state, is connected by pressure to the second actuator (16a; 16b; 16c) provided for actuating the friction-locking unit (13a; 13b; 13c) is.

Transmission device according to claim 1,

characterized in that

The directional control valve (17a, 17b) has a second control line connection (19a, 19b) which, in at least one operating state, is connected by pressure to the first actuator (15a, 15b) provided for actuating the form-fitting unit (14a, 14b).

3. Transmission device according to claim 2,

characterized in that

the directional control valve (17a, 17b) a valve spool with two, one each of the

Control line terminals (18a, 19a, 18b, 19b) associated control surfaces which are oriented in the same direction.

4. Transmission device according to claim 2 or 3,

characterized in that

The directional control valve (17a, 17b) has at least one third control line connection (20a, 20b) and the valve slide has a control surface associated with the third control line connection (20a, 20b) which is oriented in the opposite direction to the further control surfaces.

5. Transmission device according to claim 4,

marked by

a solenoid valve and a third actuator (21a) for actuating a first further coupling unit (S6a), which is connected in at least one operating condition by pressure with the third control line connection (20a).

6. Transmission device at least according to claim 5,

characterized in that

the directional control valve (17a) has at least one spring (24a) whose spring force is oriented in the same direction as the control surface corresponding to the third

Control line connection (20a) of the valve spool is assigned.

7. Transmission device at least according to claim 6,

characterized in that

the first further coupling unit (S6a) is closed in a fourth (V4), fifth (V5), sixth (V6), seventh (V7), eighth (V8) and ninth (V9) forward gear and the coupling unit (S2a; S2b; S2c ) in the eighth (V8) forward gear, in the ninth (V9) forward gear and in the reverse gear (R) is closed.

8. Transmission device according to claim 4,

marked by

a working pressure system (23b) operating in at least one operating condition

typographically connected to the third control line connection (20b).

9. Transmission device at least according to claim 8,

characterized in that

the directional control valve (17b) has at least one spring (25b) whose spring force is oriented in the opposite direction as the control surface of the valve spool associated with the third control line connection (20b). 0. Transmission device according to one of the preceding claims,

marked by

a further solenoid valve (53a) and a fourth actuator (26a; 26b; 26c) for actuating a second further coupling unit (S1a; S1b; Sic), wherein the directional control valve (17a; 17b; 17c) has a first working line connection (28a; 28b, 28c) to which the first actuator (15a, 15b, 15c) is connected and a second one

Working line connection (29a, 29b, 29c) to which the fourth actuator (26a, 26b, 26c) is connected.